Internal-combustion engine with auxiliary exhaust turbine



Sept. 14, 1954 R. DAUB 2,688,839

INTERNAL-COMBUSTION ENGINE WITH AUXILIARY EXHAUST TURBINE Filed Dec. 31, 1948 5 Sheets-Sheet l I f I! i I' II 10 IN VEN TOR.

HTTOIPNEY R. DAUB Sept. 14, 1954 INTERNAL-COMBUSTION ENGINE WITH AUXILIARY EXHAUST TURBINE 5 Sheets-Sheet 2 Filed Dec. 51, 1948 IITI'ORNEY Sept. 14, 1954 IDAUB 2,688,839

INTERNAL-COMBUSTION ENGINE WITH AUXILIARY EXHAUST TURBINE Filed Dec. 31, 1948 5 Sheets-Sheet 3 Sept. 14, 1954 R. DAUB 2,

INTERNAL-COMBUSTION ENGINE WITH AUXILIARY EXHAUST TURBINE Filed Dec. 31, 1948 5 Sheets-Sheet 4 I R. 454 dz 4 4% Ja'u Sept. 14, 1954 R. DAUB 2,688,839

INTERNAL-COMBUSTION ENGINE WITH AUXILIARY EXHAUST TURBINE Filed Dec. 31, 1948 5 Sheets-Sheet 5 W m 5 INVENTOR.

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Patented Sept. 14, 1954 UN-IT ED 5 EAT-ES N I QP-E INTERNAL-COMBUSTION ENGINE WIT-H AUXILIARYEXHAUST TURBINE Rudolph Daub, West Caldwell, 'N. J.

:ApplicationDecember 31, 1948,;Serial'=No. -68;620

tion with the accompanying drawings .illustrating the invention and in which 1 Fig. 1 is a transverse vertical sectional-view of the engine shown in'Figs. Z-and 3;v

Fig. 2 is a longitudinal vertical sectional view of anengine having four-cylindersinupright position;

Fig. 3 is a side elevationarview in outline "of the engine shown. in Figs. 1 and -2;

Figs. 4 and 5 are transverse and'longitudinal vertical sectional views respectively ofa modified form of engine; and

Fig.6 is a longitudinal vertical sectional View of another form of engine.

The invention as illustrated inFigs. 1-3 shows an upright engine comprising four cylinders which may be cast together in a'blo'ck' 8 and with a crankcase il and oil can It andseparate top valve housing M (-Fig. l). "The spark plugsare shown at 52 and the exhaust manifold l3 has-its ends receivingthe exhaust gases from' the end ports 5 it from the end cylindersand at'the center'from the exhaust port It from the intermediate .cylinders. A coupling Il =;carries the connection section ilileadingto the spiralintake casing is of. a gasturbine having the'rotor 29 on shaft'25 and exhausting into: the discharge chamber 23! passing the "gases. at. reduced "pressure into the exhaust-pipe .122. .This exhaust ing provided as shown at 36.

'the engine (Fig. 1).

.Therear endlof the crankshaft tll carriesua igear lt meshingwithagear 56 of-countershaft l-.1,-this.-..1atter..gear. 46 turn meshing with the gear lfioflcountershaft -49, gear .4 3 vloeing half the diameter of vgear 56 .so that countershaft .69 rotates .athouble .the .speed .of crankshaft 3t. .Countershaftll .is...adapted vto drive an, engine accessorysuch, for instance, has an .oil ,pump

.tfiandcountershaftlll drives the dynamic balancer indicated generally at 5|. .All .of .these parts arecarried by .a casing. 52,..53, .5 5. rigidly supported from the crankcase.

The dynamic balancer includes the. bevel --gear '55 of countershaft i9 and ,bevelgearfiedriven from gear' 55 through pinion means such asjl, the shaftsofthese gearstt. 56 running in bearings' 5 8,.59 respectively. To give .theproper balancetothe engine gear 55 carries the. semicircular weight'ti} pinned .to it. as, indicated and gear 55 carries .the segmental weight 6!, the stub shaft E2 of which runs inthe centralloearing of .gear- 55. .These .weights thus. rotate. in. opposite directions around acommonaxis parallel. to the 30. .By properly designing these weights: fit, vfil, 'thefour-cylinder engine shown may be very closely balanced against vibrational effects of the rotary parts so that it.wil1 run smoothly.

The. gears "55,158 of the balancer may also be used to 'connect the crankshaft .to engine accessories such .as the .exhaustgasturbine previously referred'to and the centrifugal supercharger'fforthe-intakeon'the opposite side of This supercharger and the gasturbine are supported'in extensions 63,64 respectively of the; crankcase 9. housing the tubular structures 65, ttthrough whichpass the shaftslt and 25-respectivelyof the supercharger and turbine. The turbine rotor 20 .throughthe 'shaft'25 drives-the bevel pinioniil meshing with the-gears "55, 56 --and-similarly the pinion 57 meshing with these gears drives the supercharger rotor 26 through the shaft 18. The housing of the supercharger is 'formedby the expanded portion 'Hwof thetubu-lar member and by the .inta'keiecasting l2:.coupled at 'l3 toa supply of gas fromthe carburetor and-passing these in take gases-sat higher pressure through the con- JThe-rotors of the lnioperation the exhausti turbine rotor it at usual speeds of the engine delivers power to the shaft I8 in the range of to of the rated horsepower of the engine so that the torque of the gas turbine is applied to the gears 55, 56 to drive the balancer and power is delivered through the gear 51' to the shaft 18 and the rotor I0 of the supercharger. The excess power of the exhaust turbine delivered to the gears 55, 56 is transmitted through shaft 49 to the gears 48, 46 and eventually to 45 depending upon the power consumption of the accessories between the gas turbine rotor and the crankshaft 30. The timing of the balancer gears 55, 56 is, of course, precisely double that of the crankshaft as determined by these gears 45, 46 and 48 and at lower speeds and lower power output of the exhaust turbine rotor, power to drive the bala-ncer 55 will be provided by the crankshaft through these gears.

The engine thus comprises a plurality of inline cylinders with relatively short connecting rods to the crankshaft and provided with a balancer including members oppositely rotating around a single axis intersecting a radius from the center of the axis of the crankpin bearing 2. The axis of the balancer members shown is also in the plane of the axes of the crankshaft and cylinders, The drawings, Figs. l-3, are to scale representing a four-cylinder engine with a cylinder bore of 3 inches and other parts in proportion.

Another typical four-cylinder, four-cycle engine of this invention having a cylinder bore of 3.750 inches and a stroke of 2.875 inches allows the use of correspondingly large valves and valve ports tending to free breathing and in addition may be under supercharger pressure as shown, with the agitating effect causing the fuel to be broken up into a fine mist thoroughly and homogeneously intermixed with the air so as to be readily ignitable even in relatively lean proportions. The short stroke of 2.875 inches keeps the piston speed for 3,600 B. P. M. within the limit of 1800 feet per minute, and also lowers the compression ratio to 6.22:1 consistent with the larger charge supplied by the supercha-rging. supercharger assembly is accessible for easy removal and replacement as is also the exhaust turbine.

structurally the engine is compact and its reciprocating masses light as compared with the usual four-cylinder in-line engine of similar bore and stroke which conventionally has a long connecting rod to minimize the unbalance.

The two-cycle engine shown in Figs. 4 and 5 has two in-line cylinders in block I08 water jacketed at I36 and having crankcase I09 and oil pan H0 and cap casing III. The crankshaft I running in bearings I has its crankpins connected by short connecting rods I32 to pistons I34 in cylinders I35 provided with intake ports I16 and exhaust ports IIB controlled by the pistons I34 of the respective cylinders. Gear I driven by the crankshaft I30 meshes with gear I48 of like diameter fixed on shaft I49 of the dynamic balancer located in the oil pan II 0 below the crankshaft, Balancing members I60, IA carried by shaft I49 have their centers of gravity 180 apart as shown and shaft I49 carries bevel gear I55 and, through pinion means I51, drives the cooperating shaft I49A carrying the balancing members I6I, IBIA corresponding respectively to members IGIJ'A and IE0 of shaft I49. The shafts I49 and I49A are coaxial with their axis in the plane of the axes of the cyl- The inders 35 and crankshaft I30. The balancing device as a whole is shown as centered with reference to the center crankshaft bearing I40 and is supported in the casing structure I53, I 54 from the crankcase I09.

Preferably the pinion I5I is used to drive an engine accessory such, for instance, as the centrifugal supercharger shown (Fig. 4), the crankcase structure being correspondingly formed as shown at I63 to house the drive members and support the supercharger casing members I'II, H2. Pinion I51 drives shaft I58 running in tubular bushing I65 and carrying gear I driving gear I8I of shaft I82 to which is fixed the rotor I'I0 of the supercharger. The air and gas mixture is received at the coupling I13 connected to the supply and is stepped up in pressure and delivered through dischargers I75 to the intakes I16 of the cylinders.

The balancing of the reciprocating parts employs members E60, A, I6! and IEIA whose torque effect counterclockwise, for instance I Fig. 5), counterbalances the unbalanced clockwise torque of the connecting rods and pistons.

Similarly the torques of the reciprocating parts of the six-cylinder, two-cycle engine outlined in Fig. 6 are dynamically balanced by the weights 260A, 260, 25I and 26IA on shafts 249, 249A driven through gear 248 at the same speed as the crankshaft 230 in bearings 24". The pistons 23 3 in cylinders 235 of block 208 are connected by rods 232 to crankpins 23L the relative angularities of which are shown in the drawing. The effect of the reciprocating parts is to create movements clockwise and counterclockwise around the center giving rise to corresponding torques which must be balanced for smoothness of operation. In the engine shown shaft 249 drives shaft 249A in the opposite direction through gears 255, 251, 256, the balancing device as a whole being mounted in casing members 253, 254 fastened to the crankcase I I9,

The balancing weights for the engines may be closely calculated to give substantially vibrationless operation. Assuming, for instance, in the engine of Figs. 1-3, pistons of about 3 inch diameter having a weight of about one pound each and adding thereto the weights of the upper end of the connecting rod, the total reciprocating weight for each cylinder would be one and onequarter pounds. The secondary shaking force for the four-cylinder engine would be 780 pounds requiring two weights 60, SI of one-half pound each on a radius of one-half inch. Similarly the weight of the masses to balance the six-cylinder, two-cycle engine of Fig. 6 would be three and one-half pounds centered on a radius of two inches. For the two-cycle, two-cylinder engine of Figs. 4 and 5 the weights would be almost the same; the different balancing effort as compared with the six cylinders would be compen sated for by different distances between the weights varying the resulting torques to accurate balancing of the engine.

I claim:

1. A four-cycle, four-cylinder internal combustion engine comprising pistons driving a crankshaft, a pair of bevel gears with cooperating pinion means between them in a plane midway between the ends of the engine, a dynamic balancing device having a pair of coaxial oppositely rotating members carried respectively by said bevel gears to rotate therewith adjacent said plane and having their common center of gravity always in said plane midway between the ends of the engine, and means for driving said bevel gears from said crankshaft at double the speed thereof.

2. An internal combustion engine as set forth in claim 1 in which a turbine driven by the exhaust of said engine is connected to said pinion means to deliver power to said bevel gears.

3. An internal combustion engine as set forth in claim 1 in which a rotary supercharger for raising the pressure of the intake gases for the engine is connected to said pinion means to be driven by said bevel gears.

4. An internal combustion engine as set forth in claim 1 in which a gas turbine driven by the exhaust-from said engine and a rotary supercharger for raising the pressure of the intake to said engine are connected to said pinion means respectively to deliver power and receive power therefrom.

5. An internal combustion engine comprising a series of cylinders having parallel axes, pistons in said cylinders driving a crankshaft having its axis in the plane of said cylinder axes, a countershaft parallel to and driven from said crankshaft, coaxial bevel gear means driven by said countershaft at double the crankshaft speed and having pinions meshing with said gear means, a gas turbine at one side of the engine receiving power from the engine exhaust from said cylinders and connected to drive said gear means through one of said pinions, and a supercharger at the other side of the engine connected to the other of said pinions to be driven from said gear means and deliver power to raise the pressure for the intake gases for the engine.

6. An internal combustion engine as set forth in claim 5 in which the bevel gear means carry on separate gears a dynamic balancing device rotating about a common axis parallel to the axis of the engine crankshaft, said dynamic balancing device having members with their common center of gravity always in a transverse plane midway between the ends of the engine.

References Cited in the file of this patent UNITED STATES PATENTS Number Name Date 1,163,832 Lanchester Dec. 14, 1915 1,984,958 Barske Dec. 18, 1934 2,127,460 Chilton Aug. 16, 1938 2,149,785 Neugebauer Mar. 7, 1939 2,248,182 Mateer July 8, 1941 2,284,515 Criswell May 26, 1942 2,359,065 Waeber Sept. 26, 1944 2,428,924 Albertson Oct. 14, 1947 

